EP0953767A2 - Machine hydrostatique - Google Patents

Machine hydrostatique Download PDF

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Publication number
EP0953767A2
EP0953767A2 EP99107900A EP99107900A EP0953767A2 EP 0953767 A2 EP0953767 A2 EP 0953767A2 EP 99107900 A EP99107900 A EP 99107900A EP 99107900 A EP99107900 A EP 99107900A EP 0953767 A2 EP0953767 A2 EP 0953767A2
Authority
EP
European Patent Office
Prior art keywords
pressure
opening
control
hydrostatic machine
regulating
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP99107900A
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German (de)
English (en)
Other versions
EP0953767A3 (fr
EP0953767B1 (fr
Inventor
Jörg Dantlgraber
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP0953767A2 publication Critical patent/EP0953767A2/fr
Publication of EP0953767A3 publication Critical patent/EP0953767A3/fr
Application granted granted Critical
Publication of EP0953767B1 publication Critical patent/EP0953767B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2042—Valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation

Definitions

  • the invention relates to a hydrostatic machine according to the preamble of Claim 1.
  • Hydrostatic machines both in axial piston design and in Radial piston designs are known in a variety of designs.
  • hydrostatic machines have a control body to the cylinders of either as a motor or as a pump working hydrostatic machine cyclically with a High pressure line and a low pressure line to connect.
  • a low pressure control opening and a high pressure control opening educated.
  • the cylinders are during the first half revolution of the hydrostatic machine with the high pressure control opening and during a second Half turn of the hydrostatic machine with the low pressure control opening connected.
  • FIG. 7 shows that of a hydrostatic machine operating as a hydraulic pump Funding volume.
  • the funding volume is the sum of the individual the cylinders passed by the high-pressure control opening Part volumes, the course of which is approximately sinusoidal. By doing sinusoidal course is missing the front hatched in Fig. 7 Flank area that is used for pre-compression to reduce pressure pulsation is needed.
  • the described delivery flow pulsation results as a result.
  • a hydrostatic machine is for one hydrostatic machine in axial piston design from DE 42 29 544 A1 and for one Radial hydrostatic machine known from DE 37 00 573 A1.
  • the control body of the hydrostatic Machine with one between the low pressure control opening and the high pressure control opening arranged to provide additional opening, which from to the cylinders leading connecting holes in the reversal area between the low pressure control opening and the high pressure control opening is briefly swept.
  • the Additional opening is connected to a pre-compression container, which in turn with the high pressure control opening or the high pressure line via a throttled Connection line is connected. With every change from the low pressure control opening the cylinders therefore become the high-pressure control opening briefly with a pre-compression volume.
  • the pre-compression volume due to the structural Size of the pre-compression container is fixed and therefore only for one Operating point can be optimized.
  • Another major disadvantage is that the course of the pressure transition from that in the low pressure control port prevailing low pressure to that prevailing in the high pressure control opening High pressure is largely undefined and the pressure of the pressure medium in the Cylinders when reaching the high pressure control port not with that in the High pressure control opening coincides with high pressure. Through the remaining pressure difference is reduced but still for the Considerable pressure and flow pulsations.
  • the invention is therefore based on the object, the noise to further reduce hydrostatic machines and a possible one To further counteract cavitation damage.
  • the invention is based on the finding that by connecting the additional opening with a regulated or controlled pre-compression device by a suitable regulation or control device is controlled, a continuous and constant pressure build-up at the transition from the low pressure control opening to the High pressure control opening can be reached.
  • the one from the pre-compression device generated pressure gradient can be particularly the speed of the hydrostatic Adjust the machine and the high pressure in the high pressure line.
  • a hydrostatic machine with variable high pressure in the High pressure line according to claim 3 advantageously provided a pressure sensor be.
  • the pre-compression device is controlled so that the Slope in the pressure build-up between low pressure and high pressure is proportional to the high pressure in the high pressure line. This ensures that the pressure builds up as slowly as possible, ensuring that the Pressure medium of the cylinder on reaching the high pressure control opening High pressure level is located.
  • a second additional opening opposite the first additional opening arranged according to claim 4 to the transition from the high pressure control port to the low pressure control port a continuous and steady To ensure pressure reduction.
  • a corresponding relief device Controlling regulating or control device can also be made according to claim 5 and 6 can be connected to a speed sensor or pressure sensor.
  • a pressure sensor be provided to the pressure gradient at the transition from the low pressure level to the high pressure level or vice versa from the high pressure level to to regulate the low pressure level continuously.
  • a sensor for detecting the displacement volume of the hydrostatic machine be provided.
  • the pre-compression device or the relief device points accordingly Claim 9 preferably a piezoelectric or magnetostrictive actuator.
  • the control of the piezoelectric or magnetostrictive actuator can be done by a Suitable electronic control circuit take place according to claim 10 a charging capacitor and a resistance element with preferably changeable Resistance can include. If the actuator is designed as a piezoelectric actuator, is the time for the electrical charge transfer between the charging capacitor and the actuator of the product of the capacitance of the charging capacitor and the Resistance of the resistance element depends. By varying the resistance of the Resistance elements can therefore be generated by the piezoelectric actuator Pressure gradient can be influenced.
  • the piezoelectric actuator generated final pressure by the charging voltage to which the charging capacitor is charged varies and at those in the high-pressure control opening High pressure can be adjusted. If according to claim 13 for the A first piezoelectric pre-compression device at the first additional opening Actuator and a second for the relief device at the second additional opening piezoelectric actuator are provided, the actuation of the actuators can also in the way that the electrical charge between the two actuators is transferred.
  • a piezoelectric actuator or a magnetostrictive actuator can also for example a magnetic pump, a mechanical pump, a hydraulic one Pressure intensifier or according to claim 14 a correspondingly controlled Control valve are used.
  • Fig. 1 shows a generally designated by the reference numeral 1, according to the invention hydrostatic machine in axial piston design.
  • Hydrostatic machines in Axial piston construction are generally known, so that the following Description limited to the essential elements here. It is emphasized that the present invention in the same way in hydrostatic machines in Radial piston design can be realized.
  • Cylinder drum 2 rotatably supported about an axis of rotation 3.
  • the cylinder drum 2 are in the form of a cylinder 4 distributed along a circle around the axis of rotation 3 provided by cylinder bores in which pistons 5 are axially movable.
  • the pistons 5 each have at their end protruding from the cylinder drum 2 a ball head 6, which in a corresponding spherical recess 7 of Slide shoes 8 is pivotally mounted.
  • the sliding shoes 8 were based on the Sliding surface 9 of a slant plate 10 and are by means of a pressure pocket 11 hydraulically relieved.
  • the swivel angle ⁇ can be determined using a suitable Adjustment device can be adjustable.
  • the cylinders 4 are by means of an Embodiment disc-shaped control body 12 cyclically alternately connectable to a low pressure line or a high pressure line. Of the Control body 12 is shown in Fig. 2 in a plan view, so that a low pressure control opening 13 and a high pressure control opening 14 can be seen.
  • the Dead center position of the pistons 5 is marked by the dash-dotted line 15.
  • the hydrostatic machine 1 works as a hydraulic pump, pressure medium during a first half revolution of the cylinder drum 2 via the low pressure control opening 13 sucked into the cylinder 4, the piston 5 a suction stroke To run. During the subsequent half rotation of the cylinder drum 2 the pistons 5 perform a pressure stroke and press the pressure medium over the High pressure control opening 14 in the connected high pressure line.
  • the hydrostatic machine 1 as a hydraulic motor is the direction of flow of the Media reversed. According to the invention is between the low pressure control opening 13 and the high-pressure control opening 14 a first additional opening 20 intended.
  • the high pressure control opening 14 asymmetrically with respect to the dead center position 15 of the pistons 5 formed so that the leading edge 21 of the high pressure control opening 14 is with respect the dead center position 15 is offset further than the trailing edge 22.
  • Equalizing the delivery volume is via the first additional opening 20 and one Pre-compression device 23 injected pressure medium into the cylinder 4.
  • the Pre-compression device 23 is used for this purpose by means of a regulating or control device 24 controlled so that in the cylinders 4 at the transition from the low pressure control opening 13 to the high pressure control opening 14 a continuous, steady Pressure builds up.
  • the pre-compression device comprises 23 a piezoelectric actuator 25.
  • the piezoelectric actuator 25 consists of several stacked ceramic disks from a piezoelectric Material, for example barium titanate.
  • the individual ceramic disks are for example by vapor deposition with electrodes and thus with a electric field that can be applied in all directions piezoelectric ceramic disks are directed in the same direction. With more suitable Orientation of the piezoelectric ceramic disks stretch when they are put on an electrical voltage. Due to the stacked arrangement of a variety of A sufficient actuator stroke can be achieved with piezoelectric ceramic plates Demand can be increased by a hydraulic translation known as such can.
  • the piezoelectric actuator 25 acts on an actuator piston 26, which in an actuator cylinder 27 is axially movable. Used to reset the actuator piston a return spring 28.
  • the actuator cylinder is connected to the first additional opening 20 via a connecting line 28 connected. If the openings 29 of the cylinder 4 shown in dashed lines over the first additional opening 20, the piezoelectric actuator 25 is moved through the Regulation or control device 24 with an increasing electrical voltage imposes that the piezoelectric ceramic plates expand and by shifting the actuator piston 26, the pressure in the actuator cylinder 27 increasing increasingly.
  • the control takes place in such a way that the pressure in the first Additional opening 20 or the cylinder 4 connected to this starting from the in the low pressure control opening 13 prevailing low pressure in the High pressure control opening 14 prevailing high pressure continuously and steadily, for example linear, increased.
  • the fact that the pressure in the cylinders 4 at Reaching the high pressure control opening 14 is at the high pressure level, pressure pulsations are avoided. Because that was needed for pre-compression Pressure medium is pressed out of the actuator cylinder 27, there are no drops in the flow of the hydrostatic machine 1, d. H. Flow pulsations do not occur.
  • the electrical voltage 25 of the piezoelectric Actuator 25 subsequently switched off, so that the piezoelectric ceramic plates of the piezoelectric actuator 25 contract and the volume of Actuator cylinder 27 enlarged again.
  • the print medium required for this can be via a suitable suction throttle 30 or a suction valve from a pressure medium tank 31 be sucked up.
  • FIG. 3 shows a top view of a control body 12 of a hydrostatic machine 1 corresponding to a second compared to the embodiment of FIGS. 1 and 2 extended embodiment. Elements already described are included matching reference numerals, so that there is a repetitive Description unnecessary.
  • a second additional opening 40 intended.
  • the second additional opening 40 is connected via a connecting line 41 an actuator cylinder 42 of a relief device 43.
  • the Relief device 43 is in the same way as the pre-compression device 23 constructed, and has a piezoelectric actuator 44, an actuator piston 45 and one Return spring 46 on.
  • the relief device 43 is controlled by a control or Control device 47 controlled.
  • For the suction of the pressure fluid is one Suction throttle 48 between the pressure medium tank 31 and the connecting line 41 provided.
  • the relief device 44 is the control or Control device 47 controlled so that in the cylinders 4 at the transition from the high pressure control port 14 to the low pressure control port 13 continuous, constant pressure reduction results.
  • the one shown in FIG. 3 The exemplary embodiment is both the first additional opening 20 and the second Additional opening 40 is provided in the dead center position 15.
  • a speed sensor 49 is provided, which is connected to the regulating and control devices 24 and 47. Furthermore, a pressure sensor 50, which is also connected to the regulating or control devices 24 and 47, is provided for detecting the high pressure prevailing in the high-pressure control opening 14 or the high-pressure line connected to it.
  • the regulating or control devices 24 and 47 generate an electrical control pulse for actuating the piezoelectric actuators 25 and 44.
  • the time interval for the rising edge to control the piezoelectric actuator 25 or the falling edge to control the piezoelectric actuator 44 is inversely proportional to the speed n of the cylinder drum 2.
  • the slope of the control pulse for the actuators 25 and 44 is further determined by the level of the high pressure p H in the high pressure control opening 14, the amplitude of the control pulse generated by the regulating or control devices 24 and 47 being proportional to the high pressure p H. It is thereby achieved that the stroke of the piezoelectric actuators 25 and 44 is proportional to the pressure difference between the level of the low-pressure control opening 13 and the high-pressure control opening 14. It is assumed that the pressure level of the low-pressure control opening 13 is essentially negligible and constant over time.
  • the speed sensor 49 can simultaneously serve to detect the rotational position of the cylinder drum 2 and thus to synchronize the actuation pulses for the piezoelectric actuators 25 and 44 with respect to the position of the openings 29 of the cylinder bores 4.
  • a pressure sensor 51 and 52 can additionally be used Detecting the actual pressure at the first additional opening 20 or at the second Additional opening 40 may be provided. This allows the rule or Control devices 24 and 47 through the piezoelectric actuators 25 and 44 certain actual pressure to a predetermined target pressure at any time of the Adjust the control pulse so that the pressure gradient in the additional openings 20 and 44 a predetermined ideal course is tracked or adjusted.
  • the swivel angle ⁇ of the swash plate 10 shown in FIG. 1 can be detected by means of a suitable sensor, for example a rotary potentiometer.
  • the swivel angle ⁇ is proportional to the displacement volume of the hydrostatic machine 1, ie the stroke volume in the cylinders 4.
  • the control signal acting on the piezoelectric actuator 25, in particular the amplitude of this control signal can be determined more precisely.
  • the regulating or control devices 24 and 47 can comprise an electrical control circuit shown schematically in FIG. 4.
  • a charging capacitor C is charged by means of a variable voltage source V via a switch S 2 to a predetermined charging voltage, which is proportional to the high pressure p H currently prevailing in the high-pressure control opening 14 and / or the displacement volume, in particular the swivel angle ⁇ , of the hydrostatic machine 1 is.
  • the switch S 2 is opened.
  • the piezoelectric actuator 25 is actuated via a resistance element R with a variable resistance.
  • the resistance R is inversely proportional to the speed n of the cylinder drum 2 detected by the sensor 49.
  • the second switch S 1 is closed and the charge of the charging capacitor C is transferred to the piezoelectric actuator 24 via the resistance element R.
  • the duration of the charge transfer is determined by the variable resistance element R, while the stroke of the piezoelectric actuator 25 is predetermined by the charging voltage of the charging capacitor C and is dependent on the high pressure p H detected by the pressure sensor 50 and / or the displacement volume of the hydrostatic machine 1 .
  • FIG. 5 shows a further exemplary embodiment of the invention.
  • A is shown Top view of the control body 12. Also here are elements already described matching reference numerals.
  • each a control valve 70 or 71 which in the illustrated embodiment is designed as a 3/2-way valve.
  • the basic position shown in FIG. 5 is that to the first additional opening 20 of the Control body 12 leading connecting line 28 interrupted.
  • With increasing Actuation of the electrical actuating device 72 becomes the connecting line 28 increasingly via a throttle 74 with the high-pressure control opening 14 or connected to the high pressure line, so that the pressure on the first additional opening 20 increasingly increased.
  • the one coming from the second additional opening 40 is the same Connection line 41 interrupted in the basic position shown in FIG. 5.
  • Valve body of the control valve 71 With increasing loading of the electrical actuator 73 Valve body of the control valve 71 increasingly displaced against the return spring 75, so that the control valve 71 opens increasingly and a relief of the second Additional opening 40 allows the pressure medium tank 31 via a throttle 76.
  • the electrical actuation device 73 is controlled by means of the control or Control device 47 in a similar manner to the control of the piezoelectric Actuator 44 in FIG. 3.
  • Fig. 6 shows the pressure p in the cylinders 4 as a function of the angle of rotation ⁇ of the cylinder drum 2.
  • the pressure profiles for conventionally designed hydrostatic machines are shown as solid lines, while the pressure profiles for a hydrostatic machine designed according to the invention are shown by dash-dotted lines.
  • the pressure pulsation in the two reversing areas can be seen in the pressure curve of a conventional hydrostatic machine.
  • the regulated or controlled pre-compression or relief according to the invention in the changeover areas achieves a continuous, steady pressure build-up or pressure reduction while avoiding pressure peaks. This can significantly reduce the noise emissions of the hydrostatic machine. Cavitation damage is also counteracted.
  • piezoelectric or magnetostrictive actuators can be used as Pre-compression device or relief device also z.
  • Legs Magnetic pump, a directly driven mechanical pump or one of a kind Electric motor with variable speed driven mechanical pump used become.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Fluid-Pressure Circuits (AREA)
EP99107900A 1998-04-27 1999-04-21 Machine hydrostatique Expired - Lifetime EP0953767B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19818721A DE19818721A1 (de) 1998-04-27 1998-04-27 Hydrostatische Maschine
DE19818721 1998-04-27

Publications (3)

Publication Number Publication Date
EP0953767A2 true EP0953767A2 (fr) 1999-11-03
EP0953767A3 EP0953767A3 (fr) 2000-08-09
EP0953767B1 EP0953767B1 (fr) 2004-07-14

Family

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Family Applications (1)

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EP99107900A Expired - Lifetime EP0953767B1 (fr) 1998-04-27 1999-04-21 Machine hydrostatique

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EP (1) EP0953767B1 (fr)
DE (2) DE19818721A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1174617A3 (fr) * 2000-07-18 2003-05-07 Liebherr Machines Bulle SA Machine hydrostatique à pistons axiaux
DE102018205884A1 (de) 2018-04-18 2019-10-24 Robert Bosch Gmbh Axialkolbenmaschine mit Druckentlastung in den Durchtriebsraum
CN111120239A (zh) * 2018-10-30 2020-05-08 罗伯特·博世有限公司 流体静力的活塞式发动机

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10135800B4 (de) * 2001-07-23 2007-08-16 Sauer-Danfoss (Neumünster) GmbH & Co OHG Druckmittelaggregat mit kontinuierlich steuerbarem Strömungsquerschnitt in der Umsteuerung
DE102008062483A1 (de) * 2008-12-16 2010-06-17 Robert Bosch Gmbh Axialkolbenmaschine mit Pulsationsminderung
DE102011117081A1 (de) * 2011-10-27 2013-05-02 Robert Bosch Gmbh Hydrostatische Kolbenmaschine
DE102014208406A1 (de) * 2014-05-06 2015-11-12 Robert Bosch Gmbh Hydrostatische Kolbenmaschine
DE102017201158A1 (de) * 2016-08-29 2018-03-01 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
DE102020212372A1 (de) 2020-09-30 2022-03-31 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatische Axialkolbenmaschine

Citations (4)

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Publication number Priority date Publication date Assignee Title
DE2152524A1 (de) 1970-10-21 1972-04-27 Citroen Sa Hydrostatische Maschine mit durch Verdrehen des Verteilers veraenderbarer Zylinderfuellung
DE2208890A1 (de) 1972-02-25 1973-09-06 Bosch Gmbh Robert Axialkolbenpumpe
DE3700573A1 (de) 1987-01-10 1988-07-21 Bosch Gmbh Robert Kolbenmaschine, insbesondere axial- oder radialkolbenmaschine
DE4229544A1 (de) 1991-09-06 1993-03-11 Voac Hydraulics I Trollhaettan Verfahren und vorrichtung zur daempfung von stroemungspulsationen bei hydrostatischen hydraulikmaschinen des verdraengungstyps

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US3199461A (en) * 1963-05-27 1965-08-10 Cessna Aircraft Co Hydraulic pump or motor
US4175914A (en) * 1977-05-31 1979-11-27 The Cessna Aircraft Company Hydraulic stop
JPS62135674A (ja) * 1985-12-09 1987-06-18 Hitachi Constr Mach Co Ltd 液圧ポンプ・モ−タ装置
DE3800900A1 (de) * 1988-01-14 1989-07-27 Rexroth Mannesmann Gmbh Schaltungsanordnung zur drehzahlregelung einer hydrostatischen maschine
JP2606758Y2 (ja) * 1992-12-22 2001-01-09 株式会社小松製作所 油圧ポンプ・モータのシリンダ室内圧力コントロール装置
DE4407282C2 (de) * 1994-03-04 1996-04-18 Hydromatik Gmbh Hydrostatischer Antrieb
US5492451A (en) * 1994-10-03 1996-02-20 Caterpillar Inc. Apparatus and method for attenuation of fluid-borne noise
US5555726A (en) * 1995-03-31 1996-09-17 Caterpillar Inc. Attenuation of fluid borne noise from hydraulic piston pumps

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2152524A1 (de) 1970-10-21 1972-04-27 Citroen Sa Hydrostatische Maschine mit durch Verdrehen des Verteilers veraenderbarer Zylinderfuellung
DE2208890A1 (de) 1972-02-25 1973-09-06 Bosch Gmbh Robert Axialkolbenpumpe
DE3700573A1 (de) 1987-01-10 1988-07-21 Bosch Gmbh Robert Kolbenmaschine, insbesondere axial- oder radialkolbenmaschine
DE4229544A1 (de) 1991-09-06 1993-03-11 Voac Hydraulics I Trollhaettan Verfahren und vorrichtung zur daempfung von stroemungspulsationen bei hydrostatischen hydraulikmaschinen des verdraengungstyps

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1174617A3 (fr) * 2000-07-18 2003-05-07 Liebherr Machines Bulle SA Machine hydrostatique à pistons axiaux
DE102018205884A1 (de) 2018-04-18 2019-10-24 Robert Bosch Gmbh Axialkolbenmaschine mit Druckentlastung in den Durchtriebsraum
CN111120239A (zh) * 2018-10-30 2020-05-08 罗伯特·博世有限公司 流体静力的活塞式发动机

Also Published As

Publication number Publication date
EP0953767A3 (fr) 2000-08-09
DE19818721A1 (de) 1999-10-28
EP0953767B1 (fr) 2004-07-14
DE59909934D1 (de) 2004-08-19

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